EP3092376B1 - Wärmekraftanlage mit wärmerückgewinnung und energieumwandlungsverfahren mit einer solchen wärmekraftanlage - Google Patents

Wärmekraftanlage mit wärmerückgewinnung und energieumwandlungsverfahren mit einer solchen wärmekraftanlage Download PDF

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EP3092376B1
EP3092376B1 EP14815620.1A EP14815620A EP3092376B1 EP 3092376 B1 EP3092376 B1 EP 3092376B1 EP 14815620 A EP14815620 A EP 14815620A EP 3092376 B1 EP3092376 B1 EP 3092376B1
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Prior art keywords
working medium
steam
condensed portion
power plant
thermal power
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German (de)
English (en)
French (fr)
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EP3092376A1 (de
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Josef MÄCHLER
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/005—Using steam or condensate extracted or exhausted from steam engine plant by means of a heat pump
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]

Definitions

  • the WO 2012/049259 A1 shows a method and system for converting an external heat source with a comparatively low temperature with a Clausius-Rankine cycle.
  • a medium in the liquid phase is compressed into a liquid medium by an external energy source.
  • the compressed liquid medium is heated by heat derived at least in part from the external heat source. This expands the medium and brings it into the supercritical phase.
  • the pressure of the heated medium is reduced to a predetermined value by labor to generate electrical energy.
  • the frequency of the energy is converted to a desired output frequency and the temperature and volume of the medium are reduced to bring the medium to the liquid phase and recycle it.
  • Several heat exchangers are provided between the liquid medium and the expanded vapor. This process is not suitable for using geothermal and solar heat due to the required temperature ranges.
  • a steam engine cycle process for converting energy using a working medium is known.
  • a working medium of high pressure and high temperature evaporated in a steam generator is expanded in a steam turbine, the exhaust steam jet being used to achieve a high condensation rate of the exhaust steam at low temperature by means of a steam jet chiller or a chiller with pre-cooling.
  • a residual steam portion that is not condensed is brought to full condensation by means of a heat pump, with the heat of condensation being transferred from the residual steam portion to the previously condensed waste steam portion.
  • the working medium is present as saturated steam after the steam expansion device only partially condensed by the throttling and the resulting cooling in the so-called "steam jet chiller", whereby the kinetic energy of the steam jet is used.
  • U.S. 2004/182082 A1 discloses a power generation system comprising a prime mover in which heated high pressure fluid is expanded in a vapor expander and the expanded fluid is directed into a collection vessel. The fluid is sucked in from the collection container by a compressor, with a non-condensed portion being sucked in directly. A condensed portion is vaporized via an expander and heat exchanger, heat of condensation of the fluid exiting the vapor expander being used to vaporize the portion expanded to a lower pressure.
  • WO 2008/009681 A1 describes the use of a cryogenic fluid for cold combustion power generation.
  • thermal power plant in particular of thermal engines, to avoid sources of heat loss, to lower the temperature required for the cycle processes used and to improve the efficiency of the plant, in particular to increase the conversion into electrical energy.
  • An energy conversion method for converting heat into mechanical or electrical energy using a working medium has the following steps.
  • a vapor state is generated in the working medium at a first pressure in a vapor generator.
  • the Evaporated working medium is expanded in a vapor expansion device to a lower, second pressure.
  • the vapor expansion device comprises two working cylinders each with inlet valves for letting in the vaporized working medium, symmetrically opposite one another and connected to a piston.
  • Energy gained through relaxation is dissipated, for example to a generator.
  • a transmission such. B. used a hydraulic transmission.
  • the expansion of the vapor state runs through a saturation line of the working medium, preferably through the critical point of the working medium.
  • the working medium is separated in a separating device into a non-condensed part and a condensed part.
  • the non-condensed portion is then compressed in a compressor to form a compressed, non-condensed portion.
  • the compressed non-condensed portion is cooled and condensed to a compressed condensed portion. Then the compressed condensed portion and the initially condensed portion are heated and the portions are returned together to the steam generator.
  • a thermal power plant for converting energy using a working medium for carrying out the method according to the invention has a steam generator for evaporating the working medium at a first pressure, a steam expansion device, each comprising two working cylinders with inlet valves for letting in the evaporated working medium, symmetrically opposite one another and connected to a piston for expansion the vapor state working fluid to a lower, second pressure, a condenser and a condensate pump.
  • Heat from combustion, geothermal energy, solar systems, waste heat from cooling systems and/or heat recovery can be used as a heat source for the working medium.
  • the condenser cools and liquefies the working fluid discharged from the vapor expander.
  • the vapor expansion device is set up in such a way that a working medium expanded by the vapor expansion device has a condensed portion and a non-condensed portion.
  • the expansion essentially runs through a polytrope of the working medium, according to the invention through a saturation line, in particular its critical point.
  • a separating device for separating the condensed part and the non-condensed part and a compressor for compressing the non-condensed part of the working medium are provided.
  • the non-condensed portion of the expanded working medium is at least partially condensed by the condensed portion in the condenser.
  • low-temperature heat such as from wood firing, geothermal sources, heat recovery, can also be converted into electrical energy with good efficiency.
  • the separating device can comprise a housing, the compressor being provided in an upper area of the housing, the vapor expansion device being provided in a lower area of the housing, and a pump for pumping off the one condensed portion being provided in a floor area below the lower area are.
  • the phase separation can, for. B. according to the centrifuge principle in a turbine.
  • the shape of the blades of the turbine is advantageously adapted for this purpose, so that the vaporized working medium is separated and the parts can be discharged from the turbine via a condensate connection and a residual steam suction line.
  • the vapor expansion device comprises working cylinders with inlet valves for admitting the vaporized working medium and pistons which are attached to the Connect the working cylinder, with two working cylinders being arranged opposite one another on the separating device. This means that two working cylinders are arranged symmetrically opposite one another and are connected to the same piston.
  • the thermal power plant preferably has a rocker arm mechanism with at least one rocker arm.
  • the rocker arm mechanism is coupled to the compressor for compressing the non-condensed portion of the working medium and a pump for draining the condensed portion from the separator.
  • the oscillating lever mechanism can advantageously be accommodated in the housing of the separating device.
  • the rocker arm mechanism can drive the working cylinders and pistons from the rocker arm mechanism.
  • a rocker arm can be coupled to the piston of the vapor expansion device and a piston of the residual vapor compressor and arranged to rotate about a lever shaft.
  • the oscillating lever is preferably also coupled to a crank drive and transfers the relaxation work of the working medium from the working cylinders to the crank drive. The crank drive can continue to deliver the work to a generator.
  • the pistons have outlet valves which are installed in the piston and can be controlled by a switch pin.
  • the switching pin is guided, for example, with the help of a link for the piston and a coupling to the rocker arm mechanism.
  • an outlet valve can be closed on one side, while an outlet valve on the other side is open and the expanded vapor can be expelled.
  • heat engines are based on a Carnot cycle according to the theory of the ideal gas with two adiabatic and two isotherms.
  • the method and thermal power plant according to the invention also involves the intermolecular attraction of the molecules, as will be explained below. As a result, an improved efficiency of the system can be achieved.
  • a working medium is first brought into a supercritical state by heat supplied from outside.
  • the supercritical working medium is then expanded through the critical point of the working medium while performing mechanical work.
  • the resulting gas/liquid phase mixture i.e. the non-condensed one, is then Part and the condensed part (residual steam / condensate) separately.
  • the residual vapor portion is first compressed and thereby heated and then brought into heat exchange with the unheated and therefore colder condensate portion, so that the residual vapor portion is liquefied.
  • the thermal power plant contains a steam generator, in which the working medium is brought into a supercritical state according to step by supplying heat, a steam expansion device for expanding the working medium, e.g. B. in the form of the working cylinder, as indicated above, or a turbine or the like.
  • a steam expansion device for expanding the working medium, e.g. B. in the form of the working cylinder, as indicated above, or a turbine or the like.
  • the supercritical working medium performs mechanical work during expansion.
  • a compressor for the residual steam and a separating device are provided, which is in fluid connection with the steam expansion device and the residual steam compressor.
  • the separating device has an upper, a lower and a base area, with the condensate portion collecting in the base area and the non-condensed residual vapor portion collecting in the lower to upper area.
  • the lower portion of the separator is fluidly connectable to the vapor expander and the upper portion is fluidly connectable to the residual vapor compressor.
  • the bottom of the phase separation vessel is in fluid communication with a pump for pumping the condensate portion back to the steam generator.
  • the residual steam compressor the residual steam is compressed and heated in the process.
  • the compressed and heated residual steam is (a) brought into heat exchange with the condensate in a heat exchanger/condenser or, in particular, (b) mixed with the condensate, the residual steam then also being condensed.
  • the vapor expansion device has e.g. B. at least one cylinder / piston unit, in particular with a boxer arrangement, and can be coupled to a generator. This will create a first part of the mechanical work performed by the supercritical working medium on the vapor expansion device is diverted to the generator in order to generate electrical energy.
  • the vapor expansion device and the residual vapor compressor are also coupled to each other, e.g. B. via a rocker arm mechanism with appropriate linkage, as mentioned above.
  • a second part of the mechanical work performed on the vapor expansion device by the supercritical working medium is used in the residual-steam compressor in order to compress and heat the residual-steam component.
  • the invention can use heat from a heat source, e.g. B. solar thermal, geothermal, etc., energy is used in such a way that in the end predominantly mechanical or electrical energy and practically no caloric energy, i.e. no significant waste heat is produced.
  • a heat source e.g. B. solar thermal, geothermal, etc.
  • figure 2 shows the Maxwell distribution 11 of the molecules for the critical point. Since the internal energy is a quadratic function of the molecular velocity, the binding energy is given at root mean square 12. The area under the curve corresponds to the proportion of molecules at the corresponding molecular speed. The area 13 on one side of the root mean square 12 corresponds approximately to the area 14 on the other side of the root mean square 12. In this state, no permanent bridge bond can set up because this is repeatedly destroyed by the faster molecules.
  • FIG 3 shows the Maxwell distribution for a final state of the working medium. After relaxation, the temperature is lower than at the beginning, which shifts the distribution function according to Maxwell 15, while the binding energy 12 is assumed to be constant. The number of molecules whose internal energy is smaller than that of the bridge bond is significantly larger. The number of molecules whose internal energy is greater than that of the binding energy is significantly smaller. You can no longer destroy all bridge bonds, so that condensation occurs. The number of condensed molecules results from the difference between the areas 16 and 17. This confirms the above approach, that condensation occurs during isentropic expansion through the critical point.
  • the thermal power plant according to the invention thus represents a type of condensation engine.
  • losses must also be considered, such as friction, leakage and insulation losses.
  • the friction will be converted into heat and this will cause condensate to evaporate.
  • the leakage losses will increase the suction volume of the residual gas compression. This results in an increasing entropy. At losses of 20%, a phase mixture of about 40% condensate and 60% steam will be achieved.
  • the heat of condensation has its maximum value at the triple point T of the working medium.
  • the value of the heat of condensation then decreases with increasing temperature and reaches zero at the critical point.
  • the principle of heat recovery by means of internal condensation according to the present invention now consists in that the vapor portion is heated by means of compression in such a way that it can be liquefied with the cold condensate portion.
  • the invention uses the effect of wet steam expansion. If the pressure at the critical point is determined from the critical density and the critical temperature of the working medium used according to the gas law, a pressure of 131 bar is obtained for air. Now the critical pressure for air is effectively 37.2 bar. This reduced pressure is explained by the effect of the intermolecular forces of attraction and this is determined with the real gas factor Z, as defined in the VDI heat atlas (1984 edition, sheet Da 13).
  • the real gas factor Z is shown as a function of the specific volume v for air in the saturation state 18, based on Table 17; Properties of air in the state of saturation, VDI heat atlas, sheet DB 11.
  • the intermolecular attraction is very strong when the density is high and the intermolecular distance is small. Immediately after the critical point, the intermolecular attraction decreases very sharply. This can result in the decrease in intermolecular attraction being greater than the increase in volume upon relaxation. In this area, the pressure can remain constant or even increase during relaxation, which must be taken into account when designing the thermal power plant. As the volume increases, the vapor changes to the gas phase.
  • figure 5 shows this relationship in a pressure-volume diagram.
  • the wet steam expansion 1 taking into account the real gas factor Z, rises immediately after the critical point 2, or the pressure increases, but then approaches the adiabatic 19, which assumes a pressure of 131 bar.
  • the pressure of 131 bar results from the general gas law from the critical temperature and the critical density of the working medium. This means that the larger the specific volume becomes, the greater the inter-molecular distance and the vapor changes into the gaseous state.
  • the adiabatic curve for pure gas expansion determined according to the general gas law, starting from the critical point, would run according to line 20.
  • the area under the state function corresponds to the work done.
  • Out figure 5 It can therefore be seen that with the wet steam expansion 1 more work is done than is the case with the pure gas expansion or the adiabatic change of state according to the line 20, starting from the critical point.
  • figure 6 is the cycle for the thermal power plant according to the invention, or the condensation engine, shown as a pressure-volume diagram.
  • the course of the wet-steam expansion is again given the reference number 1 .
  • the volume is less than 60% and the change in state due to the intermolecular attraction is flatter. This means that the compression work, caused by the intermolecular attraction, is smaller than it corresponds to the general gas theory.
  • the work in the wet steam expansion 1 cannot be determined with the adiabatic function according to the general gas law. Since no explicit function is available for the real gas factor Z, the lifting work is calculated in sections.
  • the impact process consists of two phases, the compression phase and the expansion phase.
  • the compression phase is the phase in which the force fields collide.
  • Kinetic energy is converted into potential energy.
  • the expansion phase is the phase in which the molecules push off again, the potential energy is converted back into kinetic energy.
  • the turning point of the impact process lies between the compression phase and the expansion phase. So the direction and absolute value of the velocity vector changes, as in figure 7 shown.
  • Velocity and momentum are vectors, so the energy balance per impact must be treated vectorially.
  • a molecule hits the moving piston wall 21 with an average molecular speed 22 before the impact. After the impact, the molecule has an average speed 23 .
  • the speed of the molecule, or its normal component changes by twice the piston speed (2vK), which results in a change in internal energy and a decrease in temperature, since temperature is a function of internal energy.
  • the molecule When the molecule hits the wall, the molecule is decelerated from its speed, approximately the mean molecular speed, to the wall speed. Due to this delay, it acts on the wall with an inertial force. When hitting the moving wall, this inertial force results in work with the displacement of the wall. In the expansion phase, the molecule is repelled, i.e. accelerated. Here, too, the acceleration creates a mass force with which the molecule acts on the wall, and here, too, work results from the displacement of the wall. According to the principle of conservation of energy, the work done by the molecule corresponds to the change in its kinetic Energy. The work transferred to the wall per stroke is the sum of the work done per molecular collision over the number of all molecular collisions. The number of molecular impacts on the wall can be calculated from the pressure using Newton's second principle. This calculation method was verified by using it to determine the performance of gas compressors. There was good agreement.
  • the condensation of the working medium is utilized by expansion in a thermal power plant.
  • Condensation is the transition from the gas phase to the liquid phase.
  • the molecules are free to move, they have kinetic, vibrational and rotational energy. Molecules keep colliding and exchanging momentum, according to Brownian motion. The proportions of kinetic, vibrational and rotational energy result from the degree of freedom of movement.
  • the liquid phase is based on a loose dipole bond among the molecules.
  • the molecules can still oscillate and rotate; they no longer have any kinetic energy.
  • the bridging can occur when the internal energy of the colliding molecules is less than the binding energy of the bridge. Molecules therefore condense when they collide if their internal energy is less than the binding energy of the bridge.
  • internal energy In order to condense a vapor, internal energy must be extracted from the molecules. When they hit the moving wall, the molecules are decelerated by twice the wall speed. This means that kinetic energy, resp. Internal energy is transferred to the piston, or to put it another way, internal energy is withdrawn from the molecules as they expand, allowing the vapor to condense.
  • the phase mixture separates into a condensed portion and a non-condensed portion.
  • This separation can take place by means of the principle of gravity or centrifugal action.
  • the condensate collects as a condensed portion on the floor and can be pumped out from there will.
  • the non-condensed portion in the form of the residual vapor can be sucked off at the top of the separation device, such as a phase separation vessel.
  • FIG 8 the caloric design of the condenser is shown: recooling 6 of the vapor fraction, condensing 7 of the vapor fraction on the primary side and heating 9 of the cold condensate fraction in countercurrent on the secondary side in the condenser.
  • the recooling of 60% steam with 40% condensate is possible because the specific heat of the condensate is about twice as high as that of the steam.
  • the efficiency of the thermal power plant can be explained as follows.
  • the final power delivered by the system corresponds to the difference between the work gained during expansion and the energy required for compressing the residual vapor portion and heating and pumping the condensate portion.
  • the depressurization can take place, for example, from 100 to 0.1 bar, the compression of the residual vapor fraction from about 1 to 30 bar; the mass of residual steam is between 50-60% of the expanded steam.
  • About 30% of the work generated during expansion goes into residual vapor compression.
  • the power required for pumping and heating the condensate portion corresponds to about 2% of the work gained during expansion.
  • air is preferably used as the working medium, on the one hand because it is environmentally friendly, but also because it is a well-documented medium. In principle, however, other working media, such. As ammonia, carbon dioxide or halogenated hydrogens can be used.
  • the critical point of air is at -141 °C, i.e. in the low temperature range in which air also appears as vapor and liquid or condensate.
  • FIG 9 shows schematically a thermal power plant according to the invention with a condensing engine with heat recovery.
  • the thermal power plant has a steam generator 25 with a built-in heat input device 26 .
  • the steam generator 25 is fed by a heat source 27 .
  • the heat source 27 can be: heat off Combustion, geothermal, solar systems, cooling systems, heat recovery from the system, etc. With the heat, a high-pressure steam is generated in the system and fed to a working cylinder 43 of the condensing engine.
  • the machine housing 44 acts as a separator for a condensed and a non-condensed portion of the vapor according to the invention, the machine housing 44 being a phase separation vessel.
  • the high-pressure steam is guided through a line 29 into the pressure chambers of the working cylinders 43 with cylinder heads 41 and pistons 45 .
  • the construction of the condensation engine corresponds to the so-called boxer principle, in which two cylinders 43 are arranged opposite one another on a machine housing 44 . Also installed in the cylinder head 41 are intake valves 57 for intake of vapor.
  • the pistons 45 are connected to a piston rod z. B. via a crosshead 46, which is guided in slides 47, connected to a gear with rocker arm 48 to which the lifting work of the piston 45 is transmitted.
  • the oscillating lever 48 is seated on an oscillating lever shaft 49 with which the oscillating movement is transmitted outwards to a crank mechanism 50 .
  • a transmission is driven by the crank drive 50, preferably a continuously variable hydraulic transmission, with which a generator can then be driven.
  • the rocker arm mechanism is coupled to a residual vapor compressor 51 .
  • a piston 52 in the cylinders of the residual-steam compressor 51 is driven by the rocker arm 48 via the crosshead 46 .
  • the residual vapor compressor 51 is connected to a pre-cooler 35 and a condenser 36 .
  • a piston pump 54 At the bottom of the machine housing 44 of the rocker arm mechanism is a piston pump 54 with which the cold condensate is guided to the secondary side of the condenser 36 via a line 37 .
  • a line leads from the condenser 36 back to the steam generator 25.
  • the Piston pump 54 is driven by the oscillating lever mechanism via a pump lever 55 which oscillates in a bearing 56 .
  • an electric machine acts as a motor that drives the compressor (51), pressurizes the system, expands the steam in the working cylinders (42) and thus cools the system and brings it to operating temperature.
  • figure 11 shows a cross section through the working cylinder 43 with the cylinder head 41, the cylinder head gasket 42, the high-pressure chamber in which the high-pressure steam is stored, the inlet valve 57, a valve bridge 58 into which the inlet valve 57 is screwed, a valve rod 60, a damper disc 61 with an annular groove 62, a blow-off hole 63 and a switching spring 64.
  • figure 14 shows a schematic of the control of inlet valve 57 and outlet valve 70.
  • switchover pin 69 of piston 45 moves onto switchover spring 64, thereby closing outlet valve 70.
  • annular piston 68 moves into annular groove 62 of damper disk 61 and compresses trapped steam.
  • the damper disc 61 is pushed against the cylinder flange, thereby opening the inlet valve 57.
  • the blow-off hole 63 is dimensioned in such a way that the enclosed vapor flows out at the end of the filling process and the annular piston 68 rests snugly on the bottom of the annular groove 62 . This results in a defined distance between the inlet valve 57 and the piston 45 and thus a defined filling volume.
  • figure 15 shows a cross section through the residual vapor compressor 51 with piston 52.
  • An inlet valve 73 is installed in the piston 52 and an outlet valve 74 is installed opposite, in the cylinder head.
  • a vapor outlet 75 is also provided in the flange of the cylinder head.
  • the inlet valve 73 is in a guide such. B. out a piston star 76, which is provided with an offset 77 on both sides. The offset 77 is adapted on the one hand to a shoulder of a cone of the inlet valve 73 and on the other hand to a damper sleeve 78 .
  • figure 16 shows the piston 52 of the residual-steam compressor 51 with the inlet valve 73 open.
  • the piston rod 79 is guided with the piston star 76 and has the offset 77 on both sides.
  • the damper sleeve 78 is attached to the piston rod 79 and dampens the impact when the valve 73 is closed.
  • the shoulder of the valve cone also moves into the opposite offset and thus dampens the impact when inlet valve 73 opens.
  • thermal power plant takes place in the low-temperature range, so when choosing the material for the components, special attention should be paid to the sliding problems in the mechanical parts. Good thermal insulation is also helpful.
  • a high-pressure steam is generated in the steam generator 25 .
  • this is at a temperature between 132-160K and a pressure of 37-100 bar.
  • the heat input device 26 of the steam generator 25 With the heat input device 26 of the steam generator 25, the necessary thermal energy is supplied from the heat source 27 with a suitable heat carrier.
  • the high-pressure steam generated is conducted via the line 29 into the high-pressure chambers of the cylinder heads 41, in which the high-pressure steam is fed into the displacement chambers by means of the inlet valve 57.
  • the lifting work is transmitted from the piston 45 through the piston rod to the crosshead 46, which transmits the force to the rocker arm 48 of the rocker arm mechanism.
  • the crossheads 46 are guided in links 47 so that no radial forces act on the piston.
  • the crossheads 46 are guided on rollers so that friction can be kept small.
  • the oscillating lever mechanism which oscillates on the oscillating lever shaft 49, transfers the work to the crank mechanism 50, with which a generator is driven via a further mechanism.
  • a continuously variable hydraulic transmission is preferably suitable as the transmission.
  • the residual vapor compressor 51 is also driven by the rocker arm 48 .
  • the piston pump 54 is also driven by the rocking lever 48 via the pump lever 55 which swings about the bearing 56 .
  • a phase mixture of condensed parts is formed, i. H. a condensate, and non-condensed portion, d. H. a steam portion.
  • the machine housing 44 serves as a phase separation vessel in which z. B. by means of the principle of gravity, the condensed portion and the non-condensed portion are separated.
  • the vapor portion is sucked off at the top of the machine housing 44 with the residual vapor compressor 51 and compressed. Note that only 60% of the expanded vapor needs to be recompressed, and that intermolecular attraction facilitates compression, as explained earlier. This means that this influence is to be determined with the real gas factor Z. The superheat and thus the energy balance of the process depend on this.
  • the inlet valve 57 is controlled via the damper disc 61 of the valve rod 60, as in FIG figure 11 is shown.
  • the damper disc 61 is pushed against the cylinder flange, this movement is transmitted via the valve rods 60 to the valve bridge 58 and the intake valve 57, which is screwed to the valve bridge 58, is thus opened.
  • the inlet valve 57 is cylindrical and slides a few millimeters into the cylinder bore like a piston. The pressure is thus limited by the closing spring 59 and pressure peaks which can occur at the start of the stroke can thus also be intercepted.
  • the inlet valve 57 is closed again by means of the closing spring 59 .
  • FIG 12 shows the piston 45 with an installed outlet valve 70.
  • Lubrication is difficult due to operation in the low-temperature range. Therefore, non-contact pistons 45 are provided for the condensing engine. This assumes that the pistons 45 fit relatively snugly within the cylinder bore. With a gap width of 10 ⁇ m between the cylinder bore and the piston, a leakage rate of max. 1% must be expected, with a gap of 20 ⁇ m a leakage rate of 6%. Provision is therefore made for the crossheads 46 to be mounted on rollers, so that no radial forces act on the pistons 45. So that the pistons 45 really move without contact, a centering ring 65 is provided, which is made of a material that has good dry-running properties.
  • the air trapped in the annular groove 62 flows out via the ventilation hole 62 so that the annular piston 68 rests snugly on the bottom of the annular groove 62 and there is a defined distance between the inlet valve 57 and the piston 52 and thus a defined filling quantity.
  • the compressor output is controlled in such a way that the pressure in the machine housing 44, i. H. the phase separation vessel, is about 1 bar, which corresponds to a temperature of 70K.
  • the residual steam compressor 51 the residual steam is compressed to 33 bar, resulting in a condensation temperature of 130K.
  • This heated residual vapor is introduced into the primary side of condenser 36 where it is liquefied with cold condensate supplied through the secondary side of condenser 36 .
  • At 130K there is a heat of condensation of 40.56kJ for 0.62kg of steam. If 0.38 kg of condensate is heated from 70K to 129K, 44.84kJ of heat can be dissipated.
  • the recooling of 60% steam with 40% condensate is possible because the specific heat of the condensate is about twice as high as that of the overheated steam.
  • the vapor portion can be condensed internally.
  • the resulting condensate is then returned to the steam generator 25 by means of the piston pump 54 so that there is heat recovery.
  • An electric machine can be used as a motor for commissioning.
  • the residual vapor compressor acts as a gas compressor and pressurizes the working fluid.
  • the system is controlled in such a way that in the machine housing 44, ie the phase separation vessel, there is a pressure of about 1 bar and on the overpressure side there is a pressure of at least 40 bar. This results in a pressure gradient of 1:40 in the expansion cylinder and, viewed adiabatically, cooling from 293K to 73K.
  • This allows the condensation motor to be cooled down and brought up to operating temperature. When the operating temperature is reached, condensation mode begins and the electric machine is switched to generator mode. With the pre-cooler, the compressed gas can be pre-cooled to 293K at the start.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP14815620.1A 2013-12-20 2014-12-10 Wärmekraftanlage mit wärmerückgewinnung und energieumwandlungsverfahren mit einer solchen wärmekraftanlage Active EP3092376B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH02115/13A CH709010A1 (de) 2013-12-20 2013-12-20 Wärmekraftanlage mit Wärmerückgewinnung.
PCT/EP2014/077157 WO2015091135A1 (de) 2013-12-20 2014-12-10 Wärmekraftanlage mit wärmerückgewinnung und energieumwandlungsverfahren mit einer solchen wärmekraftanlage

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EP3092376A1 EP3092376A1 (de) 2016-11-16
EP3092376B1 true EP3092376B1 (de) 2022-01-26

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JP (1) JP6293920B2 (ko)
KR (1) KR102238005B1 (ko)
CN (1) CN106062320B (ko)
AU (1) AU2014365181B2 (ko)
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CH709010A1 (de) 2013-12-20 2015-06-30 Josef Mächler Wärmekraftanlage mit Wärmerückgewinnung.
NO20180312A1 (no) * 2018-02-28 2019-08-29 Entromission As Metode for å utvinne mekanisk energi fra termisk energi
US11035260B1 (en) 2020-03-31 2021-06-15 Veritask Energy Systems, Inc. System, apparatus, and method for energy conversion
KR102598363B1 (ko) 2020-12-16 2023-11-07 홍기중 복합화력발전장치

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JPS5726215A (en) * 1980-07-25 1982-02-12 Hitachi Ltd Low boiling point medium turbine plant
DE3327838A1 (de) * 1983-08-02 1983-12-08 Genswein, geb.Schmitt, Annemarie, 5160 Düren Dampfkraftmaschinen-kreisprozess zur vollstaendigen umwandlung von waerme in mechanische arbeit, insbesondere fuer waermekraftwerke (fossil- und kernkraftwerke)
US4733536A (en) * 1986-10-22 1988-03-29 Gas Research Institute Integrated mechanical vapor recompression apparatus and process for the cogeneration of electric and water-based power having a recirculation control system for part-load capacity
DE19829088C2 (de) * 1998-06-30 2002-12-05 Man Turbomasch Ag Ghh Borsig Stromerzeugung in einem Verbundkraftwerk mit einer Gas- und einer Dampfturbine
US20020162330A1 (en) * 2001-03-01 2002-11-07 Youji Shimizu Power generating system
FR2837530B1 (fr) * 2002-03-21 2004-07-16 Mdi Motor Dev Internat Groupe de cogeneration individuel et reseau de proximite
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EP1989400B2 (en) * 2006-02-27 2023-06-28 Highview Enterprises Limited A method of storing energy and a cryogenic energy storage system
FR2904054B1 (fr) * 2006-07-21 2013-04-19 Guy Joseph Jules Negre Moteur cryogenique a energie thermique ambiante et pression constante et ses cycles thermodynamiques
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JP5596631B2 (ja) * 2011-06-30 2014-09-24 株式会社神戸製鋼所 バイナリ発電装置
BR112014003778B1 (pt) * 2011-08-19 2021-04-06 E.I. Du Pont De Nemours And Company Processo para a recuperação de calor, sistema de ciclo de rankine orgânico e método para a substituição de hfc-245fa
US9038389B2 (en) * 2012-06-26 2015-05-26 Harris Corporation Hybrid thermal cycle with independent refrigeration loop
US20140026573A1 (en) * 2012-07-24 2014-01-30 Harris Corporation Hybrid thermal cycle with enhanced efficiency
CH709010A1 (de) 2013-12-20 2015-06-30 Josef Mächler Wärmekraftanlage mit Wärmerückgewinnung.

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CN106062320A (zh) 2016-10-26
AU2014365181B2 (en) 2018-07-05
KR102238005B1 (ko) 2021-04-12
WO2015091135A1 (de) 2015-06-25
EP3092376A1 (de) 2016-11-16
AU2014365181A1 (en) 2016-06-23
KR20160101008A (ko) 2016-08-24
US10125637B2 (en) 2018-11-13
CN106062320B (zh) 2018-08-03
CH709010A1 (de) 2015-06-30
US20170002691A1 (en) 2017-01-05
JP2017501343A (ja) 2017-01-12
JP6293920B2 (ja) 2018-03-14

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